Flow regulating valve



.L Ql'll Oct. 9, 1951 E. KLEsslG 2,570,351

FLow REGULATING VALVE:

Filed June 1s, 1945 AT TO RNEY Patented Oct. 9, 1951 UNITED STATES ,PATENT vori-ICE FLOW REGULATING vALvE Ernst menig, Berkley, Mich., assignmto Vickers Incorporated, Detroit. Mich., a corporation of Michigan Application June 18, 1945, Serial No. 600,006

/ 8 Claims. (Cl. 60-52) flow at a regulated rate regardless of-load re4 Flow-regulating valves have an important use I in hydraulic power transmissions' for driving machine tools. They serve the purpose of producing a reduced speed rate of the machine tool, and the machine tool may be driven at a constant regulated rate of speed regardless of load resistance. y

In the past some difllculty was presented in preventing motor jump when the motor was started after interruption and in particular when a machine tool slide was moved into a feed position from rest or where there was a resumpy tion of a feed movementafter interruption during a slide movement. In many cases, if a feed movement was interrupted and the operator of the slide machine tool did not back the tool away from the work before resuming a cut, the tool was ruined. This is due to the fact that, when flow through the flow-regulating valve is interrupted, the compensating valve isheld to the fully open position by a compensating valve spring. When 'now is resumed after interruption, a temporary flow of fluid above the normal regulated rate Y passes through the fully open compensating valve before it is able to assume normal regulating position.Y Although this is only a momentary lapse and the compensating valve almost immediately assumes normal regulating position, this temporary dow of iluid above the normal regulated rate causes the motor to jump slightly before a constant yregulated movement begins and thus may ruin a cuttingtool.

In the past this diiculty has been avoided by the addition of valvesincorporated in the transmission to induce a flow through the flowregulating valve when flow to the motor was interrupd, thereby placing the compensating valve already in a position to regulate normally when iiow to the motor was resumed. This necessitated additional valves, lines, and fittings in the hydraulic transmission.

It is an object of this invention to provide an improved flow-regulating valve for use in a hydraulic transmission containing a fluid pump and motor which will prevent motor jump when flow is resumed through the flow-regulating valve after interruption.

It is also an object of this invention to provide a flow-regulating valve which will prevent motor jump when flow is resumed through the flow-regulating valve after interruption by preventing a iiow above the normal regulated rate before the compensating valve assumes regulating position.

It is also an object of this invention to incor- Aporate, in combination with an' adjustable throttle and compensating valve, a resiliently-loaded, pressure-responsive piston to close the compensating valve when iiow through the valve ceases vand which will gradually permit the compensating valve to assume normal regulating position in response to pressure increases when flow resumes. It is 4a further object of this invention to provide an improved flow-regulating valve which will prevent motor jump when fiow is resumed to the now-regulating valve after interruption and which may be economically manufactured, simple in operation, and which avoids the addition to the hydraulic transmission of extra valves,

lines or fittings.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawing wherein a preferred form of the present invention is clearly shown.

, In the drawing:

Figure 1 is va diagrammatic view of a hydraulic power transmission system incorporating a preferred form of the present invention. y

Figure 2 is a view corresponding to thatof Figure 1 but showing the parts in another position during operation.

Referring now to Figure 1, there is shown a pump I0 which may be driven by an electric motor. not shown, which is supplied with duid from a tank I2 by means of a conduit I4 and which has a pump delivery conduit I6 connected to a pressure port I8 of a suitable four-way directional valve 20. A cylinder port- 22 of valve 20 is connected to the rod end of a motor 24, containing a piston 25 connected to which is a rod 21, by means of a yconduit 26, and another cylinder port 28 of valve 20 is connected to the head end of motor 2l by means of a Iconduit 30. A tank port 32 of valve 20 is connected to an inlet port 34 of a flow-regulating valve 36 by means of .a conduit 38 Flow-regulating valve 3'6 also has an outlet port 40 which is connected to tank I2 by means of a conduit`42.

Incorporated in the pump delivery conduit I6 is a suitable relief valve 44 which is preferably constructed in accordance with the disclosure of the patent to Harry F. Vickers, No. 2,043,453. Valves of this character may be provided with a venting port for venting the control chamber in order to permit the main valve to act as an unloading valve and bypass the pump delivery at negligible pressure. l

A suitable manually-controlled, two-way control valve 46 is connected by means of a conduit 48 to a venting port 50 of valve 44 and to tank I2 by means of a conduit 52. In one position, valve 44 will closefventing port 50 and direct fluid from pump I to valve 20 which directs it to motor 24 to start said motor, while, in another position, valve 46 will open venting port 50 to tank I2 by means of conduits 48 and 52. permitting valve 44 to open completely and unload pump I0 to tank I2 by means of an exhaust i conduit 54 which connects valve 44 to tank |2,

thus stopping the motor 24. Relief valve 44 also serves as a safety factor in limiting the maximum pressure attainable in the system and cooperates with flow-regulating valve 36 in exhausting to tank I2 an amount of fluid from pump I0 in excess of which flow-regulating valve 36 is originally adjusted to pass.

Flow-regulating valve 36 is comprised of .a body 56 having a main longitudinal bore 58 1n which is tightly inserted a sleeve 60. Sleeve 60 has a longitudinal stepped bore 62 which'is in communication with inlet port 34 by means of an inlet passage 64 in body 56 and a groove 66 and a passage 68 in sleeve 60.

An adjustable throttle is rotatably mounted in a bore 'I2 which communicates with a passage 14 and a passage 16 at their point of intersection. Throttle 10 acts as an adjustable orifice in restricting the ow of fluid from passage 14 to passage 16. Passage 14 is in communication with bore 62 by means of a groove 18 and a passage 80 in sleeve 60. Passage 16 is in communication with outlet port 40 by means of an outlet passage 82.

A` piston 84, comprised of a stem 86 connected to which is a hollow head 88, is inserted in bores 58 and 62 with stem 86 located in bore 62 and head 88 located in bore 58. A spring 80 of predetermined tension is located in a spring charnber 82 formed in bore 58 between piston head 88 and a hollow end cap 84 threaded into the right end of bore 58. Spring 80 positions piston 84 so that a chamber 86 is formed in bore 58 between the base of head 88 and sleeve 60. A passage 88 forms a communication between inlet passage. 64 and chamber 86 so that iluid pressure in chamber 86 may act on the left side of head 88 against the resistance offered by spring 80.

Inserted in the opposite ends of bores 58 and 62 is a compensating valve |00 which is comprised of a hollow piston |02 to which is connected a stem |04 having lands |06 and |08. Stem |04 is shiftable in bore 62, and piston |02 is shiftable in bore 58. A spring ||0 of predetermined tension, located in a chamber ||2 formed in bore 58 between piston |02 and a hollow end cap ||4 threaded into the left end of bore 58, positions compensating valve |00 in bores 58 and 62 so that land |08 abuts stem 86. A chamber ||6 is formed in bore 58 between sleeve 60 and piston |02 which is in communication with groove 18 by means of a small drilled passageway ||8 in sleeve 60. When so positioned, land |08 blocks communication between passage 68 and an inlet chamber |20 formed in bore 62 between lands |06 and |08. Y

Chamber 82 is in communication withchamber I6 by means of a centrally drilled restricted passageway |22 in piston 84 and a longitudinally stepped bore |24 in the stem |04 of compensating valve |00. A branch passageway |26 of passage 16 is in communication with chamber |2. The inlet and outlet ports 84 and 40 are preferably located at the back of the body 56 and arranged for connection to the circuit lines by suitable panel mounting connectionssuch, for example, as are described in the Martin Patent No.

In operation, with the electric motor running and operating pump |0 and with pump I0 unloaded by reason of valve 44 being vented to tank |2 by valve 46, so as to stop motor 24 in the position shown in Figurevl, if valve 46 is shifted to close the venting port 50 of valve 44 and if valve 20 is shifted to connect conduit |6 to conduit 30 and conduit 26 to conduit 38, pressure fluid from pump I0 will be directed to the head end of motor 24. Fluid being forced out of the rod end of motor 24 .enters conduit 26 and is directed to the inlet port 34 of valve 36 by means of directional valve 20 and conduit 38. Fluid entering the inlet port 34 is conducted by means of inlet passage 64 and passage88 to chamber 86 where it acts upon piston head 88 against the resistance offered by spring 80. Fluid entering inlet passage 64 is prevented from entering inlet chamber |20 by means of land |08. This causes a pressure increase in inlet passage 64 which is transmittedthrough passage 88 to chamber 86.

When a suflicient pressure increase has taken place in chamber 86, which is almost instan'- taneous, piston 84 shifts slowly to the right because of the dashpot action provided by the necessity of fluid in chamber 82 having to be forced through restricted passageway |22 where it may flow to tank |2 by means of bore |24 in compensating valve |00, chamber ||6, passageway ||8, groove 18, passage 14, throttle 18, passage 16, outlet passage 82, outlet port 40 and conduit 42. Due to this dashpot action, piston 84 will shift slowly, and, as it shifts to the right, spring ||0 will shift compensating valve |08 to the right.

As shown in Figure 2, as land |88 breaks over passage 68, fluid may now enter inlet chamber |20, passage 80, groove 18, passage 14 and across throttle 10 from whence it flows to tank I2 by means of passage 16, outlet passage 82, outlet port 40 and passage 42. Pressure fluid entering inlet chamber |20 also enters chamber ||6 by means of passage 80, groove 18 and drilled passage ||8 in sleeve 60 where it may act on the right side of piston |02 against the resistance offered by spring ||0. Whatever pressure is existent in passage 16 is also existent in chamber I|2 by means of branch passageway |26 where it may act on the left side of piston |02 for causing the compensating valve ||l0l to be truly responsive to the pressure drop across throttle 10.

The purpose of compensating valve |88,- which is well known in theprior art, is to maintain a constant flow across throttle 10, and it accomplishes this by maintaining a constant pressure drop across throttle 10, and, when the pressure drop across throttle 10 slightly exceeds the resistance oiered by spring I I0, compensating valve |00 will shift to the left to partially close passage 08 to inlet chamber |20 so as to allow Just enough iluid inflow to maintain constant the pressure in chamber |20. Consequently, as piston 84 shifts to the right due to a pressure increase in chamber 88, compensating valveV will shift to the right by reason 'of spring ||0 and will gradually open up inlet chamber |08. to inletl flow from passa e 68. "igt were not for piston'84, when motor 24 was started after interruption, it would jump or move a short distance faster than flow-regulating valve 36 has been originally adjusted to permit piston of motor 24 to move. It can be clearly seen that, if motor 24 is stopped during directional movement, flow through flow-regulating valve 36 ceases. When ow through valve 36 ceases, spring ||0 would shift compensating valve |00 to the fully open position if it were not for piston 84. Thus,fwhen motor 24 was restarted, an amountiof fluid, in excess of which valve 36 has been'originally adjusted to pass, would flow through the fully open compensating valve |00 before it could shift to a normal regulating position, and this would cause motor 24 t0 lump- Itshould be, noted that compensating valve |00, when in a normal regulating position, is never wholly open or fully closed. -It can also be clearly seen that, if. at any time motor 24 is stopped-and flow through valve 36 ceases. spring 0 will shift piston 84 to the left back to the position shown -in Figure lso as to close compensating valve |00. Consequently, when motor 24 is restarted and flow.. to the flow-regulating valve 36 resumes, valve |00 is closed. As the-pressure .f

increasegto shift piston 84, compensating valve |00 will gradually open and is in a regulatingt position to maintain constant the. pressure in inlet chamber |20'. By preventing a flow of fluid above the normal regulated rate which flow-regulating valve 36 is adjusted to pass, piston 84 will prevent motor jump.

If, upon completion of movement of piston 25, valve 44 is vented to tank I2 to unload pump |0 and then motor 24 is restarted inthe opposite,

direction, fluid under 'o ressure from pump |0- will be directed tothe rod end of motor 24. When motor 24 was stopped and fluid to valve 36 ceased, piston.8 4closed compensating valve |00.

Consequently, the very same operation is again performed by piston 84. compensating valve |00 will gradually open as piston 84 shifts to the right to assume a normal regulating position and regulate the flowof fluid across,A throttle 10.

While the form of embodiment of the invention as herein disclosed constitutes a preferred form,

it is to be understood that other forms might be adopted, all coming within the scope of the claims which follow.

What is claimed is as follows:

1, A flow regulating valve for controlling the flow of fluid in hydraulic power transmission systems comprising in combination means forming va flow passage. in series in the passage an adjustsage .ahead of the compensating valve when fluid flow is resumed to the passage after interruption for effecting a gradual opening of the passage.

2. A flow regulating valve for controlling the flow of fluid in hydraulic power transmission systems comprising in combination means forming a flow passage having an inlet and an outlet, in series in the passage an adjustable throttle through which fluid is adapted to flow at a regulated rate and a pressure compensating valve, operating means for the compensating valve responsive to the pressure drop across the throttle for causing the compensating valve to assume various regulating positions to maintain the regulated flow rate "through the throttle, means for effecting a closing of the passage when fluid ilow to the inlet of the passage is interrupted, and operating means for the closing means responsive to predetermined increases of pressure at the inlet of the passage when duid ilow is resumed to the passage after interruption for effecting a gradual opening of the passage.

3. A flow regulating valve for controlling the flow of fluid in hydraulic power transmission systems comprising in combination means forming a flow passage, in series in the passage an adjustable throttle through which fluid is adapted to W at a regulated -rate and a pressure compensating valve, operating means for the compensating valve responsive to the pressure drop across the throttle for causing the compensating valve to assume various regulating positions to maintain the regulated flow rate through the throttle, and resiliently loaded means shifting the compensating valve to a position closing the passage when fluid flow to the passage is interrupted; said resiliently loaded means being responsive to predetermined increases of pressure in the passage when fluid flow to the passage is resumed after interruption for permitting the compensating valve to gradually assume a regulating position from the fully closed position.

4. A flow regulating valve for controlling the cw of fluid in hydraulic power transmission systems comprising in combination means forming a flow passage, in series in the passage an adustable throttle through which fluid is adapted to flow at a regulated rate and a pressure compensating valve, operating means for the compensating valve responsive to the pressure drop Vacross the throttle for causing the compensating valve to assume various regulating positions to maintain the regulated flow rate through the throttle.. and including biasing means tending to shift the compensating valve to the fully open position when fluid flow to the passage is interrupted, and means for overcoming the biasing means and shifting the compensating valve to a position closing the passage when iluid flow to the passage is interrupted, saidmeans being responsive to predetermined increases of pressure in the passage ahead of the compensating valve when fluid flow to the passage is resumed after interruption for permitting the compensating valve to be operated to a regulating position from the fully closed position.

5. A flowfregulating valve for controlling the flow of fluid in hydraulic power transmission systems comprising in combination means forming a flow passage, in series in the passage an adjustable throttle through which fluid is adapted to flow at a regulated rate and a pressure compensating valve, operatingY means for the compensating valve responsive to the pressure drop across the throttle for causing the -compensating valve to assume various regulating positions to maintain the regulated flow rate through the throttle, and resiliently loaded means associated with the compensating valve to close the passage when fluid flow to the passage is interrupted, said resiliently loaded means being responsive to predetermined increases o! pressure in the passage when uid ilow is resumed to the passage after interuption and coacting with the compensating valve to gradually reopen the passage.

6. A flow regulating valve for controlling the flow of iluid in hydraulic power transmission systems comprising in combination means forming a iiow passage having an inlet and an outlet, in series in the passage an adjustable throttle through which uid is adapted to ow at a regulated rate and a pressure compensating valve, operating means for the compensating valve responsive to the pressure drop across the throttle for causing the compensating valve to assume various regulating positions to maintain the regulated flow rate through the throttle, and including biasing -means tending to shift the compensating valve to a position fully opening the passage when flow to the passage is interrupted, and resiliently loaded means shifting the compensating valve to a position closing the passage when uid ilow to the inlet of the passage is interrupted, said resiliently loaded means being responsive to predetermined increases of pressure at the inlet of the passage when tluid iow to the passage is resumed after interruption for permitting the compensating valve to gradually assume a regulating position from the fully closed position. ,A

7. In a hydraulic power transmission system having a iluid pump, a iluid motor, and control means for selectively operating the motor and interrupting uid ilow to the motor for stopping the same, a ow regulating valve for controlling the speed of the motor comprising in combination means forming a flow passagel connected to the motor, in series in the passage an adjustable throttle and a pressure compensating valve, operating means for the compensating valve responsive to the pressure drop across the throttle for causing the compensating valve to assume various regulating positions to maintain the pressure drop across the throttle constant and including biasing means tending to shift the compensating valve to a position fully opening the passage when nuid now to the passage is interrupted, and resiliently loaded means shitting the compensating valve to a position closing the passage when the motor is stopped and fluid flow to the passage is interrupted, said resiliently loaded means being responsive to increases of pressure in the passage when the control means is operated to resume operation of the motor and iluid dow to the e for permitting the compensating valve to assume a regulating position from the fully closed position.

8. In a hydraulic power transmission system having a iluid pump, a iluid motor, and control means for selectively operating the motor and interrupting iluld ilow to the motor for stopping the same, a flow regulating valve for controlling the speed of the motor comprising incombination means forming a flow passage connected to the motor, in series in the passage an adjustable throttle and a pressure compensating valve, and opposing resiliently loaded means for operating the compensating valve, one of which is responsive to` the pressure drop across the throttle for causing the compensating valve to fassume various regulating positions to maintain the pressure drop across the throttle constant and thev second of which biases the compensating valve to a position closing the passage when the motor is stopped and iiow to the passage is interrupted, said second resiliently loaded means being responsive to increases of pressure at the inlet of the passage when the control means is operated to resume operation of the motor and iiuid ilow to ,the inlet of the passage for causing the compensating valve to be gradually operated to a regulating position from the fully closed position. I

ERNST KLEBSIG.

REFERENCES CITED Ihe following references are of record in the tile of this patent:

UNITED STATES PATENTS Number Name Date 2,166,940 Conradson July 25, 1939 2,313,056 AEmerson et al. Mar. 9, i943 FOREIGN PATENTS Number Country Date 373,732 Great Britain June 2, 1932 

